Motor vehicle transmission control



Aug. "9, 1938. G. T. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL Filed July 30, 1955 9 Sheets-Sheet 1 m W Ti 5 V O T m d n as a n P; Z a a v f r w y w; a Y l z Y 3 w B I 2 5 a m 2 6 4 w M 8 m 6 v 4 Q U /l. l 7 o 5 5 Mammy Aug. 9,- 1938,, O e; T. RANDoL 2,126,032

MOTOR VEHICLE TRANSMISSION CONTROL A50 By A TTORNE Y.

Aug. 9, 1938. G. T. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL 9 Sheets-Sheet 3 Filed July 30, 1935 IN VEN TOR G. TRczndoL ATTORNEY.

-Aug. 9, 1938. e. T. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL Filed July so, 1955 9 Sheets-Sheet 5 INVENTOR.

az'zzandoz A TTORNE Y.

Aug. 9, 1938. e. T. RANDOL 2,126,032

MOTOR VEHICLE TRANSMISSION CONTROL Filed July 50, 1935 9 Sheets-Sheet 6 INVENTOR.

BY 7/2. //%Z,

A TTORNEY,

Aug. 9, 1938. s. T. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL 9 Sheets-Sheet 7 Filed July 50, 1935 'INVENTOR.

.ILQ.

ATTORNEY.

Aug. 9, 1938. G. T. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL Filed July 50, 1955 9 sheets -sheet 8 INVENTOR G". 7:20 TZCZOL /;.r.

/ %Z ATTORNEY.

Aug. 9, 1938. G. 'r. RANDOL MOTOR VEHICLE TRANSMISSION CONTROL 9 Sheets-Sheet 9 Filed July 30, 1935 I INVENTOR.

G. 7.72arzdoZ/ ATTORNEY.

Patented Aug. 9, 1938 MOTOR VEHICLE PATENT OFFICE TRANSMISSION CONTROL Glenn '1. Randoi, Marmaduke, Ark. ApplicationJuly 30, 1935,;Serial No. 33,900

71 Claims.

This invention relates to an improved motor vehicle transmission control of the general character disclosed in Patent No. 1,687,591 issued to me October 16, 1928.

The invention seeks, as a salient object, to

provide a mechanism wherein a single initial setting of the control handle will serve for all forward speeds beginning either with low or second speed and wherein, after reaching high speed, subsequent automatic operation of the mechanism will cause the two highest speeds,

namely, second and high, to alternately function until neutralized or until low speed is again rendered active, following which latter the same cycle of successive operations will again occur, thereby reducing the necessity for manual manipulation on the part of the driver to a minimum.

A further object of the invention is to provide a mechanism wherein a single hand operation will serve to render reverse active and also wherein a single hand operation will serve to set the mechanism for neutral, which neutral setting is effective for and common to all speeds.

The invention seeks, as another object, to provide a mechanism wherein low and reverse may be selected and rendered active by manually operable means exclusively; wherein low and reverse may be neutralized manually or automatically .by power actuated means and wherein, if so desired, the power actuated means may be employed to assist the manually operable means in neutraiizing either low or reverse.

The invention seeks, as a further object, ,to

provide a mechanism which may be manually set to automatically select second speed and high speed successively; wherein both speeds may be successively rendered active or neutralized exclusively by power actuated means, automatically, and wherein the usual clutch pedal may, if so desired, be actuated to supplement the-power actuated means in rendering either speed active or inactive.

Still another object of the invention is to provide a mechanism which, after being manually set, will automatically function to select second speed and render said speed operative; wherein upon the ensuing actuation of the mechanism, second speed will be automatically neutralized and high speed automatically selected and rendered active; wherein upon the ensuing actuation of the mechanism high speed will be automatically neutralized and second speed automatically'selected and again rendered active, the functioning of the mechanism being such that a mechanism wherein, when manually set to function automatically, second speed will always be initially selected and rendered active automatically sothat second speed will always be caused to function prior to the use of high speed. I A further object of the invention is to pr'ovide a mechanism wherein all speeds may be automatically neutralized.

Still another object of the invention is to provide an improved power actuated toggle mechanis'm through which the force will be transmitted for rendering active second and high speeds or neutralizing all speeds; wherein the toggle will, during the first half of its active throw, impart a movement of gradually diminishing speed to the gear being neutralized but conversely, during the second half of its active throw will impart a movement of gradually increasing speed toa selected gear being rendered active while, as the toggle crosses dead center, the parts affected will be caused to momentarily pause to permit the usual gear synchronizing mechanism'to function prior to positive engagement of a selected gear and wherein the toggle may be adjusted 'to suit the axial gear travel of difierent transmissions as well as to, compensate for wear.

And the invention seeks, as a still further object, to provide a mechanism adapted to supplant the present hand control assembly of conventional types of sliding gear and constant mesh transmissions, the present mechanism being such that the control of the various speeds is dependent upon the will of the driver, thereby enabling the driver to keep the performance of the vehicle at a point of maximum efliciency and economy of operation, which features are greatly sacrificed through the use of the more expensive and complicated types of so called automatic transmissions which utilize for their operation "some characteristic of either engine or car performance.

Other and incidental objects of the invention not specifically mentioned in the foregoing will appear during the course of the following description and in the drawings which form part of this application.

Figure 1 is a plan view of my improved mechanism in neutral, parts being broken away and shown in section. t

Figure 2 is a fragmentary side elevation showing the power control valve in normal position.

Figure 3 is a plan view showing the selector levers swung inwardly and high gear selected.

Figure 4 is a section on the line 4-4 of Figure 3 showing the control valve moved upwardly to admit suction to the forward end of the power cylinder and simultaneously admit air to the rear end of said cylinder.

Figure 5 is a plan view showing the selector levers swung outwardly and one of the shifters carried forwardly to render high gear active.

Figure 6 is a section on the line 6--6 of Figure 5 showing the floating pin of the valve which accommodates forward movement of the clutch pedal while the valve remains stationary.

Figure 7 is a longitudinal sectional view through the mechanism in neutral.

Figure 8 is a section on the line 8-6 of Figure 7. p

Figure 9 is a fragmentary plan view showing the control slot as seen from the line 9-9 of Figure 7.

Figure 10 is a transverse section on the line ll0 of Figure 9.

Figure 11 is a fragmentary rear elevation of the mechanism. a

Figure 12 is a transverse section on the line l2-l2 of Figure 5.

Figure 13 is a transverse section on the line l3l3 of Figure 5.

Figure 14 is a detail section showing the coupling plunger of one of the shifters engaged in a neutral groove of the selectors.

Figure 15 is a detail section showing the coupling plunger engaged in a socket of one of the selectors.

Figure 16 is a fragmentary section on the line l6-|6 of Figure '5.

Figure 17 is a detail section on the line I 'I--I I of Figure 16 particularly showing the ratchet mechanism and one of the setting pawls therefor.

Figure 18 is a detail section showing the setting pawl of Figure 17 engaged with one of the pins of the ratchet.

Figure 19 is a detail section on the line I9-i9 of Figure '7.

Figure 20 is a detail plan view partly in section and showing a step in the movement of the toggle employed in conjunction with the selector levers.

Figure 21 is a view similar to Figure 20 and showing another step in the movement of the toggle.

Figure 22 is a perspective view of the selectors.

Figure 23 is a detail section particularly showing the coupling plunger.

Figure 24 is a fragmentary detail elevationof the control valve, and

Figure 25 is a detail View partly in section and partly in elevation'particularly showing the outer side of the high and second gear shifter.

In carrying the invention into effect, I employ a casing l0 which, as seen in Figure 13, is provided at the left side thereof with a reduced extension I and in this connection, it may be noted that the arrows of the section line l3l3 of Figure point toward the front end of the casing and the terms right and left as used herein will be predicated accordingly. Formed on the casing at its lower side is a bottom flange I2 which, as seen in Figure 1, is shaped to fit over a conventional transmission case, as conventionally shown at l3 (Figure 7), supplanting the usual transmission case cover and, as will be observed, the flange I2 is apertured to receive the usual bolts which ordinarily secure the transmission casecover so that, as will be appreciated, the casing l0 may be readily mounted in operative position. At its forward end the casing is, as seen in Figures 1 and 7 of the drawings, reduced in width and stepped to provide a shelf l4, and closing the casing at its upper side is a removable cover plate l5.

Inserted through the rear end wall ofthe easing is a pair of removable rods l6 and I! which, as shown in Figure 11, are slotted at their rear ends and screwed to said end wall of the casing is a locking plate l8 provided at its ends with oppositely presented lugs engaging in the slots of the rods for locking the rods against rotation as well as against endwise movement. Formed in the lower side of the rod l6 medially thereof, as shown in dotted lines in Figures 1, 3 and 5 of the drawings, is a neutral notch IS, a low speed notch 20 and a reverse notch 2 I. The rod I1 is similarly provided with a neutral notch 22, a second speed notch 23 and a high speed notch 24 Slidable on the rods l6 and I! are gear shifters and 26, the shifter 26 being individually shown in Figure 25 of the drawings. Near opposite ends thereof, these shifters, as seen in Figures 1 and 13 of the drawings, are provided with thickened bosses which form heads, the head of the shifter 25 being indicated at 21 and the head of the shifter 26 being indicated at 28, and formed on the shifters at their lower margins are parallel vertical flanges 29. It is now to be observed, as particularly seen in Figures 1, 5 and 13 of the drawings, that the side walls of the casing l0 are provided medially with inclined portions which form longitudinal abutments 30 each having angularly disposed inner faces and, as best brought out in Figure 13, the heads 21 and 28 of the shifters are cut away to provide seats fltting the angularly disposed faces of the abutments to rest flat thereagainst. The abutments will thus limit the shifters against rotative movement on the rods l6 and I1 and are of a length equal to the endwise travel of the shifters to coact with said rods for slidably supporting the shifters for endwise movement within the casing l0. Depending from the rear end of the shifter 25, as seen in Figure 12, is a fork 3| and depending from the forward end of the shifter 26 is a fork 32, these forks extending into the transmission case to operatively engage the proper sliding gears of the transmission and in this connection, it should be observed that the gear engaged by the fork 3| is movable forwardly by the shifter 25 for low speed and rearwardly by said shifter for reverse while the gear engaged by the fork 32 is movable rearwardly by the shifter 26 for second speed and forwardly by said shifter for high speed.

As shown in Figure 13, the head- 21 of the shifter 25 is slotted at its lower side and pivoted in said slot is a rocker 33. Seated in a suitable socket in the head to coact with one end of the rocker is a spring 34 and coacting with the opposite end of the rocker is a detent 35 slidable through the head to yieldably coact with the rod I6 under the influence of the spring 34. Figure 13 of the drawings shows the shifter 25 in neutral position notch 20 of said rod while, when the shifter is moved rearwardly for rendering reverse active, the detent will ride out of the notch 2i. Thus, the detent will act on the shifter for yieldably locking low speed active or reverse active as well as yieldably locking the shifter in neutral position. Secured to the instrument board of the vehicle adjacent the steering post, as seen in Figure 7, is a sleeve which extends through the vehicle dash and is appropriately anchored adjacent its lower end tothe engine housing. Slidable longitudinally in said sleeve as well as rotatable therein is a control rod 31 to the upper end of which is fixed a handle 38 and rotatably connected to the lower end of said rod is the shaft of a flexible cable 39, the construction being such that only endwise movement can be imparted to said shaft by the rod. Upstandirg from the rear end of the shifter 25, as seen in Figure-l, is a lug 4d and screwed into said lug is a stub shaft M having a fiat face N. Screwed into the rear end wall of the casing it is a sleeve 43 which slidably accommodates the stub shaft ll and, as will now be observed, the adjacent end of the sheath of the cable 39 is detachably connected to the outer end of said sleeve while the adjacent end of they flexible shaft of the cable is'welded into a'suitable socket in the outer end of the stub shaft M.- The control rod- 3l is thus operatively connected with the shifter 25 while by applying a joined by-a transverse connecting portion 55.

Fixed to the control rod 37! for movement in said slot is a stop pin dll.

Normally, the shifter 25 stands in middle neutral position, as shown in Figure l, in which position of said shifter, the pin 3? is disposed midway of the long side fi l of the h-slot in the sleeve 35 at the connecting portion 46 of said slot. The handle 38 may then be said to be in neutral position since, as will presently appear, the position of the pin 41] just indicated is neutral for all speeds. As will be seen, the handle 35 may, when the pin til is at the portion 46 of the slot, be rotated clockwise to the right to dispose the pin M in the long side M of the slot or counter-clockwise to the left'to dispose the pin M in the short side 55 of the "slot. For convenience of description, the

right {or long side Ml of the h-slot will be referred to as the manual side while the short or left side of said slot will be referred to as the automatic side. For the same reason like terms will also be usedin connection with the handle 33, the handle being turned to the manual side when rotated to the right and being turned to the automatic side when rotated to the left while, when the handle is turned to the manual side and is in middle position, the handle is, as just above noted, in neutral.

Assuming now that the shifter 25 stands in neutral position, it will be seen that when the handle 38 is turnedto the manual side, said handle may be actuated for shifting the rod 3'! downwardly and moving the gear shifter 25 forwardly for rendering low speed active, as preagainstthe bottom walls of the sockets.

viously described, while, when the handle is returned to its initial position, low speed will be neutralized. Conversely, by pulling on the handle. the rod 31 may be shifted upwardly for moving the gear shifter 26' rearwardly and rendering reverse active while, when the handle is returned to its initial position, reverse will be neutralized. I accordingly provide a means whereby low and reverse may be manually selected, manually rendered active and manually neutralized.

Removably secured in position by the locking" plate l8, as particularly seen in Figure 1, is a ro-' tatable selector shaft 48, journaled at its ends in suitable bearings. This shaft is disposed midway between the rods l6 and Il parallel thereto and slidably flttin'g said shaft is a pair of companion selectors 49 and 50, shown in detail in Figure 22 second speed socket 5d. The selector 50 is substantially a counterpart of the selector 45 andincludes a pair of sector-shaped fingers which, as seen in Figure 13 of the drawings, digitate with the fingers M of the selector 45 about the shaft 45 so that the several fingers provide .a cylindrical surface around the shaft and formed in one of the fingers 55 is a suitable keyway to receive a key 56 locking the selector 55 to turnwith the shaft M. Thus, as the fingers 55 inter-ergage with the fingers 59 of the selector 55, both selectors are locked to turn with the shaft. The fingers 55 like the fingers 5|| are integrally connected at their outer ends by an end ring or head and screwed or otherwise detachably connected to the fingers 55 is a collar 5i cooperating with said end ring to provide an annular groove 55 around the selector near the outer end thereof. Formed in each of the fingers 55 adjacent the collar 5i is a high speed socket 55.

As shown in Figure 13, the head 25 of the gear shifter 25 is slotted at its lower side and pivoted in said' slot is a rocker Bil like'the rocker 35.

- Formed through the lower portion of the head,

as seen in detail in Figure 13, is a square opening and slidably fitting in said opening'is a square plunger Bl, the plunger being thus locked against rotation. Interposed between the lower end of the rocker Eli and said plunger is a spring 62 one end of which is accommodated in a suitable socket in the plunger and, as will be noted, the plunger is formed at its outer end with a reduced tip 53 of a thickness somewhat less than the width of the sockets 54 and 59 in the fingers of the selectors to provide corresponding play between these parts.- As brought out in Figure 22, the end walls of the sockets 54 and 59 are fiat to engage the fiat faces of the tip 63 of the plunger while the bottom walls of said sockets are concave, the tip of the plunger being provided with a convex end face so as to seat flat This construction provides an arrangement whereby, when the selectors are shifted, as will be presently described, the plunger 6! will, when engaged in any one of the sockets 54 and 5,9, serve to effectually couple the gear shifter 26 with either.

one 'or the other of said selectors, as the case, may be while, when the selectors are rotated, the

plunger will readily ride out of said sockets. Slidable through the head 28 to coact at one end with the upper end of.the rocker 60 and at its opposite end with the rod 11 is a detent 64, the plunger 6| and the detent 64 being both actuated by the single spring 62,

When the selectors are shifted outwardly away from each other to normal retracted position, as seen in Figure 1, the fingers and 55 of said selectors still provide a cylindrical surface against which the plunger 6| rests so that at no time will the plunger ride off of said fingers to become displaced by the spring 62. At the meeting longitudinal edges of the fingers, the outer corners thereof are cut away to provide concave neutral grooves 65 extending longitudinally of the fingers and of a length somewhat greater than the endwise travel of the selectors. These grooves are thus located 90 apart midway between the sockets 54 and 59 of the selector fingers and, as shown in Figure 14, are adapted to selectively receive the tip 63 of the plunger 6| when the selectors are rotated to, neutral position, as will be presently described.

When the selectors 49 and 50 are shifted inwardly toward each other, as shown in Figure 3, it will be noted that the fingers 5| and 55 of said selectors do not project beyond the outer ends of the selectors. In thus forming the selectors with overlapping fingers, ample endwise travel of the selectors is possible .while, at the same time, the structure is compact. Furthermore, it will be noted that when the selectors are shifted inwardly, the sockets 54 and 59 in the fingers of said selectors are brought into circular alignment to selectively receive the plunger 6| as the selectors are rotated while between said sockets are disposed the neutral grooves 65 to selectively receive the plunger as the selectors are turned to a point midway between each pair of adjacent sockets. It is thus possible to employ but a single plunger upon the gear shifter 26 to coact with both selectors for coupling the shifter either to the selector 49 for endwise movement therewith to render second speed active or to the selector 50 for endwise movement therewith to render high speed active, as will be later explained. Normally, the detent 64 will, as shown in Figure 14, be engaged in the notch 22 of the rod I! for yieldably locking the shifter 26 in neutral position. When the shifter is moved rearwardly, the detent will ride out of the notch 22 and engage in the notch 23 for yieldably locking second speed active while, when the shifter is moved forwardly from neutral position, the detent will ride (fit of the notch 22 and engage in the notch 23, as shown in Figure 13, for yieldably locking high speed active.

Pivoteol at its outer end to the rear end wall of the casing in, as shown in Figure 7, is an interlock lever E56 detachably mounted by a cap screw 6? in a plane midway between the gear shifters 2 a and 2t. At its inner end this lever is, as shown indetail in Figure 19, provided with a T 'head 6S and formed in the parallel vertical flanges 29 of the gear shifters 25 and 26 are sockets 69 which, when said shifters are centralized within the casing in neutral position, are disposed opposite each other in alignment with the T head The head is, as will be noted, of a length greater than the distance between said flanges so that when either gear shifter is moved from neutral position, the socket in the flange 29 thereof will coact with the adjacent end of the head for rocking the lever and engaging the other end of the head in the socket in the flange of the other gear shifter, when the head will be confined between said flanges. Accordingly, as will be seen, the construction provides a means for automatically locking either gear shifter in .neutral position as the other shifter is moved so that by no possibilitycan both shifters be moved at the same time to render more than one speed active.

Journaled through a suitable bearing in the bottom wall of the extension ll of the casing !0, as particularly shown in Figure 12, is a veriically disposed shaft 10. opposite which is similarly mounted a like shaft ll. -Keyed to the upper end of the shaft I0 is a selector lever I2 and freely mounted upon the upper end of the shaft H is a coacting selector lever 13. The free ends of these levers extend over the selectors 49 and 50 and depending from said levers are studs '54 tors will be moved inwardly to the position shown in Figure 3 while, when the levers are swung apart, the selectors will be shifted outwardly to normal position as shown in Figures 1 and 5. Extending laterally from the hub of the lever 72 is an arm 75 notched at its free end and extending laterally from the hub of the lever i3 is an arm 16 rounded at its free end to engage in said notch so that the levers are thus coupled to swing in unison.

Pinned to the lower end of the shaft is a toggle lever ll having a bore 18 \therein which extends through the hub of said lever while at its free end the lever is provided with a yoke l9. Pinned to the lower end of the shaft H is an operating lever 8|] from the inner end of which extends a short integral toggle lever 8| in which is formed a substantially L-shaped slot 82 having a short leg 83 and a long leg 84. The short leg provides a shoulder 85 but, as will be observed, the outer wall of the slot is'curved at the junction between the legs. Connecting the levers Ti and 8| is a, link indicated for convenience as a whole at 86. This link is formed of complemental sections one of which is provided with a cam head 81 from which extends a shank 88 and rising from said head is a cam peak or lug 89. The head 81 is freely accommodated between the sides of the yoke 19 of the lever ill and pivotally connecting the head with said yoke is a pin 90. The other section of the link comprises a yoke 9| which straddles the lever 8| and connecting said yoke with said lever is a pin 92 which is freely accommodated through the slot 82. The yoke 9| is screwed on the shank 88 for adjustment thereon and locking. the yoke in adjusted position is a jam nut 93. Inserted in the bore 18 of the lever H is a spring 94 abutting the shaft l0 and freely movable in the bore is a ball detent 95 urged by said spring to coact with the cam head 81 of the link.

As previously noted, the free ends of the levers i2 and i3 normally stand apart, as shown in Figure 1, and this figure of the drawings also shows the normal set position of the toggle. In this position of the parts, the pin 92 of the link 86 is seated in the short leg 83 of the slot 82 to coact with the shoulder 85 while the ball detent 95 is disposed forwardly of the cam peak 89 to coact with the cam head 8'! for maintaining the pin 92 seated as well as holding the link firm and it will now be assumed that the lever cc is i the shaft 2,126,082 swung forwardly. As will be perceived, the le-- as'shown in Figurs 3, for shifting the selectors 48 and 58 inwardly to the end of their throw.

During this first portion of the travel of the lever 88, the lever 11 and link 86 function as a toggle and as the pin 82 is, in the meantime, traveling in an arc with the lever 8|, the link 86 is coincidently rocked on the pinv 88. Accordingly, the carrl head 81 is pivoted relative to the ball detent 85 until the forward face of the cam peak 88 is brought into engagement with said detent. The detent will thus coact with said face of the cam peak for urging the link 86 clockwise and resisting any'tendency of the pin 82, due to the pushing tlirustthereon, to ride out of engagement' ,with the shoulder 85. As the pin 82 travels into line with the shaft II and pin. 88, this tendency of the ball detent to swing the link clockwise is progressively increased as the-ball detent rides up the forward face of the cam peak tocompress thespring 84 so that, as shown in Figure 3, when the free ends of the levers 12 and I3 reach the end of their inward throw and the selectors 48 and 58 are accordingly shifted inwardly to the limit of their movement, the ball detent 85 will, when the toggle reaches dead center, coact with the forward face of the cam peak near the tip of said peak for firmly maintaining the link in position to receive the pushing thrust thereon to the extreme end of its pushed travel.

As the forward swinging movement of the lever 88 then continues, the pin 82 will be swung ,dead center by the lever 8| while the ball detent 85 will remain engaged with the forward -face of the cam peak 88 adjacent the tip thereof to still urge the link 86 clockwise and maintain the pin 82 seated in the short leg 83 of the slot 82.

As soon as the pin 82 crosses dead center, the short leg of the slot will begin tomove away from the pin 88 but the clockwise thrust of the ball detent 85 on the link 86 will continue until, as the lever 8| is swung forwardly by the lever 88 to pull on the link, the link is rocked pin 88 by the lever .8| to ride the cam peak 88 across said detent and break the toggle. The ball detent will then coact with the rear face of the link, as shown in Figure 20, to exert a counter-clockwise thrust on the link which thrust, however, will be overcome by the pull of the lever 8| on the link. Thus, as the lever 88. continues forwardly in its swinging movementto the end of the throw thereof, the lever 8| will pull on the link 86 for swinging the lever 11 toward the shaft H and swinging the free ends" of the levers l2 and 13 outwardly to the end of their throw, as shown in Figure 5, to shift the selectors 48 and 58 outwardly to normal position.

Figures 5 and 20 of the drawings show the operating lever 88 at the end of its forward throw and it will now be assumed that said lever is returned rearwardly. Immediately as, the lever 88 starts to travel rearwardly and the lever 8| thus begins toswing therewith, the short leg 83 of the slot 82 will begin to travel in an are away from the pin 82 while said pin will, due to the counter-clockwise thrust exerted on the link 86 on the a when the lever 8| is swung toward the pin 88, such travel of the lever 8| is accommodated by the long leg 84 of the slot, in which leg the pin 82 freely rides.

As the rearward travel of the lever 88 continues, the lever 8| will, of course, act on the pin 82 for rocking the link 86 on the pin 88 so that the pin 82 will be returned across dead center while the cam peak 88 will be returned across the ball detent 98 to again act against the forwand face of said cam peak to exert a clockwise thrust on the link. Accordingly, as the lever 88 approaches the end of its rearward throw and the short leg 83 of the slot 82 again becomes accessible to the pin 82, said pin will -be snapped, by the ball detent acting on the link, into said leg of the slot for resetting the toggle ready to function when the operating lever 88 is next swung forwardly.

Attention is now particularly directed to the fact that the one-way forward movement of the operating lever 88 is converted by the toggle into a two-way movement of the levers 12 and 13 for first shifting the selectors 48 and 58 inwardly and then returning the selectors outwardly to normal position while upon the return throw of the operating lever, the toggle is automatically reset without moving the selector levers or disturbing the selectors. Furthermore, it is to be noted that the force required to swing the levers I2 and 13 for shifting the selectors is transmitted directly through the toggle not only to swing the levers toward each other but also to swing said levers apart.

Referring again to Figures 1 and 3 of the drawings, it will be seen that the rate of travel imparted to the levers l2 and I3 by the toggle will be greatest at the inception of the movement of said levers toward each other and will gradually diminish as the toggle approaches dead center so that a corresponding diminishingrate of shifting movement will be imparted to any gear being neutralized by the selectors 48 and 58. The manner in which the gears are neutralized will be presently explained. Conversely, the rate of travel imparted by the toggle to the levers 12 and 13 will, as will be appreciated upon reference to Figures 3 and 20 of the drawings, be

least at the inception of movement of said levers apart and will gradually increase as the pin 82 approaches the forward end of its arc of travel so that a corresponding increasing rate of shifting movement will be imported to any gear being rendered active by either of the selectors 48 and 58. The manner in which the gears are so rendered active will be presently explained. Furthermore, after the levers l2 and 18 reach the of a selected gear, As will be appreciated, by adjusting the yoke 9| on the shank 88 of the toggle link 86 the effective length of said link may be varied for varying the throw of the levers I2 and 13 to suit the axial gear travel of different transmissions as well as to compensate for wear.

Journaled through a suitable bearing in the shelf I4 adjacent the forward end of the shaft 48, as seen in Figure 7, is a vertically disposed shaft 96 to the lower end of which is fixed a lever 91 and depending from said shelf are spaced pins 98 and 99 for limiting the lever in its swinging movement. Freely mounted on the upper end portion of the shaft 96 is a bevel gear I00. At its forward end, the shaft 48 is reduced and fixed to the reduced portion thereof to mesh with the bevel gear I is a bevel gear IOI, said gears being of a 2 to 1 ratio. Upstanding from the gear I00 are four long ratchet pins I02 equi-distantly spaced circumferentially of the gear and upstanding from said gear at points midway between the long pins L02 are four short ratchet pins I03. The relative length of these pins is best shown in Figures 7 and 16 and, of course, the several pins are disposed 45 apart. It is now to be observed that the lever 13 is somewhat longer than the lever I2 and pivoted to the forward end of the lever 13 at its lower side is a pawl I04 detachably mounted, as particularly seen in Figure 13, upon a screw stud I05. Coiled around the head of said stud is a spring I06 one end of which is anchored to a suitable lug upon the inner edge of the lever I3 while the opposite end of the spring engages over the outer edge of the pawl I04. As best seen in Figure 16 of the drawings, the pawl extends over the gear I00 to' rest thereon and, as will be appreciated, the spring I08 will urge the free end of the pawl to coact with the ratchet pins I02 and I03.

Mounted on the sleeve 36, as shown in Figure '7, is a lever I01 having a hub I08 surrounding said sleeve and formed in the upper side of the sleeve beneath the hub, as shown in Figure 8, is a transverse slot I09. Formed in the lower end portion of the control rod 31. at its upper side is a longitudinally extending groove I I0 and extending through the hub' I08 of the lever I01 is a stop screw III which projects through the slot I09 in the sleeve 36 and at its inner end is provided with a smooth stud H2 which is freely received in the groove IIO of the rod 31, the stop screw being secured in position by a suitable jam nut. Thus, when the control handle 38 is turned to rotate the rod 31, the lever 101 will be swung by the stop screw l I I which will travel in the slot I 09 while, however, when the handle 38 is operated to shift the rod 31 endwise to control low and reverse as previously described, the

' stop screw III will coact with the walls of the slot I09 for limiting the lever I0I against lat,- eral movement with the rod. Extending between the lower end of the lever I01 and the'free end of the lever 91 is a rod 3 which, as seen in Figure 8, is detachably connected with said levers.

Fixed to the upper end of the shaft 96 is a lever H4 and pivoted to the free end of the lever at its lower side, as shown in Figure 16, is a pair of superposed pawls comprising a long pulling pawl I I5 and a short pushing pawl I IS, the relative length of these pawls being seen in Figure 3. Urging the pawl II5 to coact with the ratchet pins I02 and I03 is a spring II! and removably fixed at one end in a suitable recess in the adjacent wall of the casing I0 to coact with said pawl is a deflector finger I I8 extending at its free end into the path of travel of the pawl. Urging the pawl IIB to coact with the ratchet pins 102 and I03 is a spring I I9 and, in this connection, it may be observed that said pawl rides at all times against said pins.

In the neutral position of the handle 38, the lever 91 stands engaged with the stop pin 98 so that the lever I I4 is swung to the position shown in Figure 1 when the pivoted ends of the pawls H5 and H8 serve to hold the pawl I04 away from the ratchet pins I02 and I03 in inactive position. Furthermore, when the mechanism is in neutral, as shown in Figure 1, the selectors 49 5 and 50 stand retracted while the gear shifters 25 and 26 stand centralized within the casing. It is also to be particularly noted that when the mechanism is in neutral, the tip 83 of the plunger 6| stands engaged, as shown in Figure 14, in one of the neutral grooves 65 of the selectors. Assuming therefore that the operating lever 80 is swung forwardly, as previously described, the pawl I04 will not function as the levers I2 and I3 are swung while the plunger tip will, as the selectors 49 and 50 are shifted, ride in said neutral groove. Thus, the neutral setting of the mechanism will remain unaffected.

Assuming now that the handle 38 is turned to the automatic side, it will be seen that the lever 91 will be swung to engage the stop pin 99 so that the lever II4 will be swung to the position shown in Figure 5, away from the pawl I04 to ride the pawl H5, as shown in Figure 17, onto the finger H8. The pawl II5 will thus be held inactive by said finger while the pawl I04 will move to active position to coact with the ratchet pins I02 and I03 and, in this connection, it may be noted that as the plunger 6| yieldably bears against the selectors 49 and 50 at all times, said plunger will consequently hold the selectors and therefore the shaft 48, against any free rotative movement with the result that the loose gear I00 will be locked by the gear IOI against any free rotation.

Clockwise rotation of the gear I00 by the pawl I 04 will, of course, turn the shaft 48 in a counterclockwise direction and as the pins I02 and I03 are 45 apart, the active throw of the pawl will turn said gear 45 and consequently turn the shaft 90 to correspondingly rotate the selectors 49 and 50. Thus, as the sockets 54 and 59 in the selector fingers are spaced 90 apart, the selectors will be rotated step by step by the pawl I04 to receive the plunger tip 63 in said sockets successively.

As will be presently explained, the selectors 49 and 50 are, when the handle 38 is turned to neutral, always rotatably set to receive the tip 63 of the plunger 6| in one of the neutral grooves 65 and as these grooves are disposed midway between the sockets 54 and 59 in the fingers of the selectors 49 and 50, the plunger will rest either in a neutral groove 45 ahead of the high speed socket 59 of one fingerof the selector 50 or in a neutral groove 135 ahead of the high speed socket of the other finger of said selector.

It is now to be noted that as the short pawl H6 is disposed on top of the pawl II5, only the long pins I02 of the gear I00 are, as brought out in Figure 16, of sufiicient height to be engaged by the short pawl and when the mechanism is in neutral, the short pawl will, as shown in Figure 1, be retracted by the lever II4 to the end of its throw ready to engage any long pin I02 disposed in the path of its active movement. As will be perceived, the plunger BI is, in the position of the parts shown in Figure l, engaged in the neutral groove 65 which is disposed 45 in advance of the high speed socket 59 of one of the fingers of the selector 50 and attention is directed to the fact that only oneof the long pins I02 of the gear I is disposed in the path of the active throw of the pawl I I6 which pin, in the position of the parts. indicated, lies 22% from the end of said throw. Accordingly, when the handle 38- is turned to .the automatic side and the lever I I4 is swung, as previously described, the pawl I I6 will engage the long pin I02 indicated and rotate the gear I00 clockwise 22 /2 with the result that the shaft 48 will be turned counter-clockwise 45 and the selectors correspondingly rotated to dispose the high speed socket of the selector finger indicated in line with the plunger 63. Thus, when the operating lever 80 is swung forwardly, as previously described, and the levers I2 and 13 are swung inwardly, the pawl I04 will engage one of the ratchet pins I02 and I 03 and rotate the selectors 90", as previously described, to dispose the second speed socket 54 of the next succeeding finger of the selector 49 in position to receive the tip 63 of, the plunger 6| as the selectors reach the end of their inward movement. Theplunger tip will then, of course, engage in said socket of the selector 49 for coupling the shifter 26 to said selector so that, as the levers l2 and I3 are swung apart and the selectors are returned to the end of their outward movement, the shifter 26 will be moved rearwardly to render second speed active.

Assuming now'that when the mechanism is in neutral, the plunger 6i is engaged in the neutral groove 65 of the selectors which is disposed 135 in advance of the high speed socket 59 of the next succeeding finger of the selector 50. In this position of the parts, one of the long pins I02 of the gear I00 will be disposed in the path of the active throw of the pawl H6, 67 from the end of said throw and as in the instance previously described, only a single long pin will lie in said path. In this connection, it may be noted that the long pins I02 are, of course, properly positioned circumferentially of the gear I00 in relation to the position of the fingers of the selector 50 and as the selectors and the gear will always turn in unison, the relation between the pins and said selector fingers will not change. Furthermore, it is to be noted that the 2 to 1 ratio between the gear I00 and shaft 45 will compensate for the difference between the number of long pins on the gear and the number of fingers on the selector 50 so that while but a single long pin will, at any one time, be disposed in the path of the active throw of the pawl H6, some one of said pins will, when the plunger is engaged in the neutral gronve 65 45 in advance of the next succeeding high speed socket, always reach a point 22 from the end of the active throw of the pawl I I6 while, when the plunger is engaged in the neutral groove 135 in advance of the next succeeding high speed socket, some one of the long pins will always be moved to a position 67 from the end of the active throw of the pawl H5. Continuing, therefore, with the instance last taken, it will be seen that when the plunger 63 is engaged in the neutral groove 135 in advance of the next succeeding high speed socket of the selector 50 and the handle 38 is turned to the autoline with the plunger. Accordingly when the selector 49 so that as the levers 12 and 13 are swung outwardly to the end of their throw, the

shifter 26 will be moved rearwardly for rendering second speed active.

As will thus be seen in view of the foregoing description, I provide means operable by the handle 38 such that when said handleis turned to the automatic side, the selectors 49 and 50 will be rotatably set in such a position that,

upon the ensuing operation of the mechanism, second speed will always be initially selected automatically and rendered active. Assuming therefore, that the handle 38 is pushedforwardly on the manual side for rendering low speed 'active and is then returned for neutralizing lowv speed. as previously described, when the handle is turned to the'automatic side, it will be seen that second speed will always be automatically selected and rendered active following low speed.

When the handle 38 ispushed forwardly on the manual side, the operator will, of course, be able to feel the detent 35 drop into the low speed notch 20 while, when the handle is pulled rearwardly to neutralize-said speed, the operator will be able to feel said detent drop into the notch i9; Similarly, when the handle is pulled rearwardly from neutral position for rendering reverse active, the operator will be able to feel the detent 35 drop into the reverse notch ZE. The operator will thus be able to tell when low speed has been rendered active, when reverse has been rendered active or when either low speed or reverse has been neutralized so that the handle 99 may be shifted without any attending uncertainty on the part of the operator as to the effect produced by the movement of said handle I said pin may cross through the connecting portion 46 of the h-slot.

Assuming now that second speed has been automatically selected and rendered active, as previously described, it will be seen that when the operating lever 80 is next swung forwardly, the selectors 49 and 50 will be rotated by the pawl I04 as the levers l2 and 13 are swung inwardly but as long as the plunger GI remains engaged in the registering second speed socket of the selector 49, the shifter 26 will be returned to-- ward neutral position by the plunger. It is to be noted, however, that the collars 52 and 51 of the selectors are disposed to engage the selector heads 21 and 28 so that as the levers I2 and 13 swing inwardly, the collar 52 0f the selector 49 will engage the head 28 of the shifter 26 for returning said shifter to neutral position as shown in Figure 3, and. consequently neutral-.

izing second speed. coincidentally, the selectors will be rotated 90 by the pawl 104 so that as the selectors reach the end of their inward movement, the high speed socket 59 of one of the fingers of the selector 50 will be disposed to receive the plunger (ii. The plunger will then, of course, drop into said socket forcoupling the shifter 26 with the selector 50 so that as the forward movement of the operating lever 80 continues and the levers l2 and I3 are swung apart, the shifter 2'6 will, as shown in Figure 5, be carried forwardly with the selector 50 to render high speed active.

It will now be assumed that high speed is active and that the operating lever 80 is again swung forwardly. As will be appreciated, the plunger ti will, as long as said plunger remains engaged in the registering high speed socket of the selector 59, return the shifter 26 toward neutral position but as the collar 51 of said selector is disposed to engage the shifter head 28, the collar will coact with said headfor returning the shifter 26 to neutral position and neutralizing high speed. Coincidentally, the selectors 49 and 50 will be rotated 90 by the pawl 104 so that as the selectors reach the end of their inward movement, the second speed socket 54 in one of the fingers of the selector 49 will be moved into position to receive the plunger 6|. The plunger will then, of course, drop into said socket for coupling the shifter 26 with the selector 49 so that as the forward movement of the operating lever 80 continues and the levers 12 and I3 are swung apart, the shifter 25 will be carried rearwardly by the selector' 49 for again rendering second speed active.

It will thus be seen that as long as the handle 38 remains on the automatic side, the mechanism will function, upon the initial actuation thereof, to automatically select and render active second speed, that upon the next actuation of the mechanism, second speed will be autothe automatic side, the pawl I i5 stands, as previmatically neutralized and high speed automatically selected and rendered activefthat upon the next actuation of the mechanism, high speed will be neutralized and second speed again automatically selected and rendered active, and so on indefinitely.

It will now be assumed that either second speed or high speed is active and that the handle 38 is turned to the manual side in neutral position. As will be seen, the lever H4 will be swung from the position shown in Figure 3 back to the position shown in Figure 1 for rendering the pawl Hi4 inactive while the lever 9,! will be swung to again engage the stop pin 98 and in this connection, attention is directed to Figures 17 and 18 of the drawings. When the handle 38 is on ously noted, on the finger H8, as shown in Figure 17-, in inactive position but as the. handle is turned to neutral, as just assumed,- the pawl will ride off of said finger and, as shown in Figure 18, engage the first of any one of the pins H12 and it?) disposed in the path 'of the active throw of the pawl so that as the lever H4 is returned to the end of its throw, as shown in Figure 1, the gear mt will be rotated counter-clockwise. Due to the length of the finger i 18, the working throw of the pawl H5 is 22 and as there are eight pins but only four neutral grooves 55, the number of pins will compensate for the 2 to 1 ratio mtween the gear and gear it! so that regardless of whether second speed is active or high speed is active, some one of the pins m2 and W3 said throw. Accordingly, when the handle 38 is turned from. the automatic side to neutral position and the lever H4 is swung, the pawl H5 will turn the gear I09 counter-clockwise 22 with the result that the selectors 49 and 50 will be rotated clockwise 45". Thus, if at the time, the plunger 6| is engaged in one of the sockets 54 of the selector 49, the tip 63 of the plunger will be caused to ride out of said socket, as the selectors are rotated to engage in the neutral groove 55, in advance of the next succeeding high speed socket 59 of the selector 5!] while, if at the time, the plunger BI is engaged in one of the high speed sockets 59 of the selector 50, the tip 63 of the plunger will, as the selectors are turned, be caused to ride out of said socket to engage in the neutral groove 65, 45 in advance of the next succeeding high speed socket 59. It will accordingly be seen that when the mechanism is neutralized, the plunger 61 will rest either in the neutral groove 65, 135 in advance of the next succeeding high speed socket or in the neutral groove 45 in advance of the next succeeding high speed socket, as previously indicated.

Continuing, therefore, with the assumption that when either second speed or high speed is active, the handle 38 is turned from the automatic side to neutral position, it will be seen that the selectors 49 and 50 will be rotated to engage the plunger 6| in one of the neutral grooves 65 of the selector fingers so that when the operating lever 80 is next swung forwardly and the selectors 49 and 50 are moved inwardly, the collar 52 of the selector 49 will, if second speed is active, engage the head 28 of the shifter 26 for returning said shifter to neutral position and neutralizing second speed while, if high speed is active, the collar 51 of the selector 50 will engage said head for returning the shifter 26 to neutral position and neutralizing high speed, the plunger 6! meantime riding inactive in said neutral groove. Accordingly, either secondspeed or high speed will, if active, as the case may be, be automatically neutralized.v

Assuming'that low speed is active, it will be seen that when the lever 80 is swung forwardly, the collar 51 of the selector 50 will engage the head 21 of the shifter 25 for returning said shifter to neutral position and neutralizing low speed. Similarly, when reverse is active and the oper; ating lever 80 is swung forwardly, the collar 52 of the selector 49 will engage the head 21 of the shifter 25 for returning said shifter to neutral position and neutralizing reverse. Thus, as will be perceived, not only second and high'will be automatically neutralized by the mechanism, as previously described, but also, low and reverse may, instead of being manually neutralized, as previously'described, be automatically neutralized if so preferred. In any event, however, if the handle 38, after having been pushed for wardly for rendering low speed active, is allowed to remain in its forward position, low speed will be neutralized upon the actuation of the operating lever 80. Similarly, if the handle 38 is allowed to remain in its rear position after having been manually operated for rendering reverse active, reverse will be automatically neutralized upon the next actuation of the operating lever 80.

As previously explained, the handle 38 may, while either second or high speed is active, be turned to neutral position for preselecting neutral for subsequent automatic neutralization of the mechanism and attention is now directed to the fact that, after the handle 38 has been turned to the automatic side, the stop pin 41 may travel forwardly in the short side 45 of the h-slot so that said handle may be pushed forwardly when on the automatic side for manually selecting and rendering active low speed prior to the automatic selection and rendering active of second speed,

- as previously described. Thus, after the handle 38 has been pushed forwardly on the automatic side, no further attention need be given thereto as, when the operating lever 80 is next actuated, low speed will, as previously described, be automatically neutralized sothat the handle 38 will be returned to middle position on the automatic side, after which second speed will be automatically selected and rendered active, followed by high speed in the manner. previously explained. As long as it is desired to have the mechanism function automatically, the handle will be permitted to remain in middle position on the automatic side. It will be noted, however, that the mechanism may be easily and quickly neutralized at any time simply by turning the handle to the manual side in neutral position.

vAttention is now directed to Figures 14 and 15 of the drawings. As will be noted, the neutral grooves 65 of the selector fingers are more shallow than the high and second'speed sockets 54 and '59 of said fingers. Accordingly, when the plunger 6| is engaged in any one of the neutral grooves 85,

as shown in Figure 14, the spring 62 is correspondingly compressed and the pressure of said spring on the detent 64 is correspondingly increased for holding the shifter 28 against movement. Conversely, when the plunger 6| is engaged in any one of the sockets 54 and 59, as shown in Figure 15, the pressure of the spring 62 on the detent 64 is correspondingly relieved to facilitate the movement of said shifter for rendering a speed active or inactive. Thus, when theselectors 49 and are rotated to cause the plunger tip 63 to drop into one of the sockets 43 and 50 as shown in Figure 15, the spring tension on the detent 64 will be relieved so that said detent may readily ride out of the neutral notch 22 in the rod I! while, however, the spring tension on the plunger BI will be entirely sufficient to hold the plunger tip engaged in said socket so that the plunger will effectually couple the gear shifter with either of the selectors for movement thereby. Assuming; however, that when either second speed or high speed is active, the handle 38 is turned 'to neutral, the selectors will, as previously explained, be rotated to engage the plunger 6| in one of the neutral grooves 65, as

shown in Figure 14. The gear shifter 26 will thus be uncoupled from the selector with which it was engaged but, as previously noted, the spring tension on the detent 64 will be increased so that if the shifter is in its rear position, said detent will be urged by the increased pressure of the spring to firmly engage in the notch 23 of the rod I! for yieldably locking second speed active while, if the shifter is in its forward position, said detent will be urged by the increased pressure of the spring to engage in the notch 24 of said rod for yieldably locking high speed active. When the handle 38 is turned to neutral and the selectors are rotatably set to engage the plunger 6| in one of the neutral grooves 65 of the selector flngers,-the operator will of course be able to feel the plunger drop into said groove as the handle reaches the end of its turning throw so that no uncertainty will exist as to whether or not the object sought has been accomplished.

Fixed to any appropriate part of the vehicle adjacent the transmission is an arm I28 and pivoted to the free end of said arm, as particularly seen in Figure 1, is a power cylinder I2I which is preferably provided with removable heads I22. Projecting from the forward head of the cylinder are ears I23 which receive clamping rods I24 and formed on said rods are hooks I25 engaging over the rear .cylinder head, the rods being equipped at their forward ends with nuts adjustable for clamping the cylinder heads in position on the cylinder shell. Screwed through the rear head of the cylinder axially thereof is an eye-bolt I26 and extending through the eye of said bolt and through the arm I20 is a bolt I21 pivotally connecting the cylinder with said arm.

Reciprocable in the cylinder is a piston including a piston rod I28 slidable through the front head of the cylinder and removably mounted on said rod is a piston head, indicated for convenience as a whole at I29. Adjacent its rear end, the piston rod is provided with a stop shoulder I38 and screwed on the rear end of the rod is ,a nut I3I. Interposed between said shoulder and the nut is a pair of circular resilient clamping plates I 32 and clamped between said plates are leathers I33. As will be observed, the plates I32 are provided, in spaced relation to the periphery thereof, with annular oppositely bowed portions while the peripheral margins of said plates are flared oppositely to coact with the leathers so that when the nut I3I is adjusted, the major portion of the clamping pressure of said plates will be exerted at the flared peripheral margins thereof on the peripheral margins on the leathers for effectually supporting the. leathers to coact with the wall of the. cylinder. At its forward end, the piston rod I28 is provided with a yoke I34 which is pivotally connected to the free end of the operating lever 80 by a removable 'pin I35 and adjustable on the forward end portion of the piston rod is a nut I36 between which and the yoke is clamped one end of a flexible boot I31, the opposite end of which is secured to the front cylinder head about the piston rod bearing therein for protecting said bearing as well as enclosing the forward end portion of terposed between the front cylinder head and the piston head I29 is a volute spring I38 urging the piston rearwardly within the cylinder I2I and, as will now be observed, the piston rod I28 will engage the eye-bolt I26 for limiting the piston in its rearward movement. Accordingly, the eyebolt I26 may be adjusted on the rear cylinder head for varying the throw of the piston to suit the throw of the operating lever 88 with relation to the position of the arm I28 and, of course, the cylinder will rock on said arm as the lever 80 is swung.

At its forward comer, the extension II of the casing III is formed with a flat seat I33 and.

detachably bolted to said seat is, as particularly seen in Figures 4, 5 and 6 of the drawings, a

cylindrical vertically disposed valve casing I48 Formed in the valve casing below the nipple I42 the piston rod. In-

and in angular relation thereto, as particularly seen in Figures 1 and 2 of the drawings, is a compound nipple I44 and extending between said nipple and the front and rear ends respectively of the cylinder I2I are upper and lower pipes I45 and I46, which are flexible.

Slidable in the valve casing I is a tubular valve rod I41 shown in detail in Figure 24 of the drawings. The rod is, as particularly shown in Figure 6, closed at its upper end and rising therefrom, as seen in Figure 5, are spaced stop lugs I48 to engage the upper end wall of the casing for limiting the rod in its upward movement. Bisecting the lower end portion of the rod is a longitudinally extending slot I49 and extending transversely between the lower ends of the prongs thus formed is a stud I50. Slidable freely within the valve rod is a pin I5I and interposed between the upper end of said pinand the end wall of the rod is a spring I52 urging the pin downwardly. Formed in the exterior of the valve rod, as seen in Figure 24, is a longitudinally extending upper slot I53 opening onto the upper end of the rod between the stop lugs I46 and formed in the rod adjacent said slot is an L-slot having a narrow portion I54 extending parallel to the slot I53 at one side thereof and a wide portion I55 extending circumferentially of the rod beneath the lower end of the slot I53. Formed in the rod below the portion I55 of the L-slot is a lower slot I56 aligning with the slot I53. As will be observed, the portion I54 of the L-slot is disposed for registration with the port of the suction pipe I43 while the portion I55 of said slot is adapted to register with the spaced upper and lower ports of the pipes I and I46 as are also the slots I53 and I56. I

The usual clutch pedal shaft of the vehicle is indicated at I51 and fixed thereon is the usual clutch pedal I51 and a bell crank embodying a.

lever I58 which extends upwardly and a lever I59 which extends rearwardly at a right angle to the former lever. As seen in Figures 4 and 13, the

lever I59 extends at its rear end freely throughthe slot I49 in the valve rod I41 above the stud I to coact with the lower end of the sliding valve pin I5I so that, as will be seen, the valve rod thus floats in the casing I40 on the spring I52 but is locked against rotation by the lever I59.

-Swiveled on the operating lever 80 is an eyebolt I60 and pivotally connected to the upper end of the lever I58 is a rod I6I which is slidably received through the eye of said bolt and is provided at its rear end with a stop nut I62 adjustable thereon for varying the effective length of the rod, a jam-nut also being preferably employed.

When-the clutch pedal I51 of the vehicle stands retracted in normal position, the control valve and associated parts also stand in normal position, as shown in Figures 1 and 2 of thedrawings. As will be observed, the valve rod I41 is at the bottom of its throw so that the narrow portion I54 of the L-slot lies below the port of the suction pipe I43-, the rod thereby closing said port, while the wide portion I of said slot lies below the port of the pipe I46. -Both of the latter ports are, however, in communication with the slot I53 in the valve rod so that air is thus admitted through the port I4I, through said slot and through the pipes I45 and I46 to both ends of the cylinder I2I. The piston I29 will thus rest at the rear end of its throw under the tension of the spring I30. It is also pointed out that, in the normal position of the clutch pedal, the stop nut I62 on the rod I6I stands away from the eye'- bolt I a distance sufficient to permit the clutch pedal to be rocked forwardly to disengage the clutch without actuating the lever 60, approximately the first third of the forward throw of the rod IGI being idle. In this connection it may be noted that the first third of the forward throw of the clutch pedal is utilized to disengage the clutch while the second third of said throw is utilized to cause the shifting of the transmission gears. The last third of the forward throw of the clutch pedal is not utilized but provision is made whereby the pedal may freely continue to rock forwardly to the end of its throw.

It will now be assumed that the clutch pedal I51 is rocked forwardly for the first third of its throw to disengage the vehicle clutch. As will be seen, the operating lever 80 will remain at rest, as previously described. The lever I59 will, however, be caused to coact with the valve pin I5I for; lifting the valve rod I41 approximately half of its upward throw to middle neutral position. As a result, the slot I53 will first be moved out'of communication with the port of the pipe I46 for cutting off the admission of air to.the rear end of the cylinder I2I when the wide portion I55 of the L-slot will be brought into communication with the port of said pipe. Engine suction will then be communicated through the pipe I43, the L-slot and through the pipe I46 to the rear end of the cylinder I2I but as, at the time, the piston I 29 will, as previously noted, be at rest at the rear end of its throw, no movement will be imparted to the piston. As the valve rod I41 continues upwardly, the wide portion I55 of the L-slot will move out of register with the port of the pipe I46 and when the clutch pedal reaches the end of the first third of its forward throw and the vehicle clutch is disengaged, will be disposed at a level between the ports of the pipes I45 and I46. Consequently, when the valve rod is in middle neutral position, as just described, engine suction through the pipe I43 will be cut ofi. The slot I53 in the valve rod will, however, remain in communication with the port of the pipe I45 for admitting air to the front end of the cylinder, as previously described, while the slot I56 in the valve rod will be moved into communication with the port of the pipe I46 so that air will thus flow through the slot I56 and through the pipe I46 for relieving the partial vacuum behind the piston I29. Thus, as will be seen, the clutch pedal of the vehicle may be freely operated throughout the first third of its throw for disengaging the vepower actuated piston and connected parts so that any gear at the time selected will remaln'undisturbed.

Assuming now that the clutch pedal I51 is rocked further forward from the end of the first third of its forward throw to the end of the second third of its forward throw, it will be seen that the lever 'I 59 will, as shown in Figure 4 of the drawings, continue in its upward travel to coact with the valve pin I5I and lift the valve rod I41 to the end of its upward movement, when the stop lugs I48 will engage the top wall of the valve casing I40 for limiting the valve rod in its upward travel. As will be perceived, the slot I53 in the valve rod' I41 will be moved out of communication with the port of the pipe I45 after which the wide portion I55 of the L-slot will be moved into communication with said port while the slot I56 of the valve rod will remain in communication with the port of the pipe I46. Accordingly, admission of air to the front end of the cylinder I2I through the pipe I45 will be cut of! following which engine suction will be communicated through the pipe I43, through the L-slot and through the pipe I45 to the front end of the cylinder while air will be admitted through the slot I56 and through the pipe I415 to the rear end of the cylinder. Thus, the piston I29 will be shifted forwardly in the cylinder I2I to compress the spring I38 and swing the operating lever 80 forwardly to the end of its throw.

It will now be assumed that the clutch pedal I51 is rocked further forward from the end of the second third of its forward movement to the end of its throw. As shown in Figure 6, the lever I59 will be swung further upward from the position shown in Figure 4 to coact with the pin I5I and shift saidpin upwardly within the valve rod l,4'l.independently thereof to compress the spring I52, the spring accommodating the independent travel of the valve pin. Thus, the valve rod will be held at the limit of its upward travel while, however, the clutch pedal will be permitted to freely move forwardly from the end of the second third of its forward travel to the end of its throw.

Upon the release of the clutch pedal 957' said pedal will, of course, be immediately returned to normal position by the usual clutch spring while the spring I38 will urge the piston I29 rearwardly. Throughout the first third of the return travel of the clutch pedal, the valve pin I5I will, underthe action of the spring I52, move downwardly within the valve rod I41 to follow the lever I59, the valve rod I41 in the meantime remaining at the limit of its upward throw. During the second third of the return travel of'the clutch pedal, the 'valve rod I41 will move downwardly within the valve casing I40 to middle neutral position when, as previously described, air will be admitted to the front end of the cylinder I2I for breaking the partial vacuum therein while air will also be admitted to the rear end of the cylinder. ,As the clutch pedal then continues to move rearwardly for the last third of its return throw, the slot I56 in the valve rod I41 will be moved out of communication with the port of the piped for cutting off admission of air to the rearend of the cylinder, after which the wide portion I55 of the L-slot of the valve rod will move into communication with said port, the slot I53 of the valve rod in the meantime remaining in communication with the port of the pipe I45.

Thus, air will be admitted to the front end of the cylinder I2I while engine suction will be communicated through the pipe I43, through the L- slot and through the pipe I 45 to the rear end of said cylinder for shifting the piston I29 rearward-' 'ly to the end of its throw, after which, as the clutch pedal reaches the end of its return move- -ment and the valve rod I41 comes to rest at the of the power cylinder and coincidentally admitting air to the rear end of said cylinder so that the suction operated piston will be shifted forwardly foractuating the operating lever 89 while, upon I the return throw of the clutch'pedal, the valve f is operable thereby for admitting suction to the rear end of the power cylinder and coincidentally active, it will now be seen that when the clutch.

pedal is actuated, the power actuated piston I 29 will be caused to function for first neutralizing low speed automatically when second speed will be automatically rendered active. Upon the next actuation of the clutch pedal, second speed will be automatically neutralized, when high speed will be automatically rendered active. Upon the next actuation of the clutch pedal, high speed will be automatically neutralized and second sped again automatically rendered active, second and high speeds being thus alternated as long as the handle 38 is permitted to remain on the automatic side. When the handle is turned to neutral, however, either second speed orhigh speed, as the case may be, will, upon the next actuation of the clutch pedal, be automatically neutralized, as will now be understood, for neutralizing the transmission. Assuming that the handle 38 has been pushed forwardly on the manual side and low speed is'active, it will now also be seen that, when the clutch pedal is next actuated, low speed will be automatically neutralized. Accordingly, low

be employed to supplement the hand control and the same is true 'of reverse. Furthermore, it is to be noted that as either high or second speed is rendered active, the clutch pedal may, if so desired, be employed to supplement the action of the power piston. As previously pointed out, approximately the flrst third of the forward throw of the rod IBI is idle so that the control valve will be moved to admit engine suction to the front end of the power cylinder just before the stop nut I62 engages the swiveled eye-bolt H50. Consequently, the piston I 29 will then begin to move forwardly but, as will be perceived, the clutch pedal may, if so desired, be moved to engage the nut I62 with said eye-bolt, when forward pressure on the clutch pedal will be communicated to the lever 80 swinging the'lever forwardly auxiliary to the power piston and, as will be appreciated, the clutch pedal may, should the control valve or power piston fail, be utilized alone for swinging said lever to render either second or high speed active or inactive.

Having thus described the invention, I claim:

1. In transmission control mechanism, rotatable digitated selectors having sockets in the fingers thereof and axially shiftable to dispose said sockets in circular alignment, shifting means movable by said selectors selectively for rendering a selected speed active, coupling means carried by said first-mentioned means and engageabie in said sockets selectively when disposed in alignment for coupling said shifting means with said selectors selectively for movement thereby, and means for rotating said selectors to dispose said sockets selectively in position to receive said coupling means.

2. In transmission control mechanism, rotatable selectors having overlapping fingers forming a cylindrical surface and provided with sockets, 

